JPH1078045A - Torsional vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid generation of unexpected friction moment. SOLUTION: For a torsional elastic unit 33, an elastic unit contact arm extended in the nearly radial direction relating to an axial line A is provided, and relating to a first shock absorber member 14, 16 and a second shock absorber member 12, an intermediate ring element 42 rotatable around the axial line A is provided, the elastic unit contact arm is arranged in the peripheral direction between mutually opposed end parts of at least two elastic units 32 of an elastic unit, the intermediate ring element further includes a radial direction motion preventing means for preventing the elastic unit 32 from moving to the radial direction outer side in an end part region facing the elastic unit contact arm.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a torsional vibration damper for damping torsional vibrations in a power transmission system of an internal combustion engine, in particular for a clutch disk.
fer). The torsional vibration damper comprises a disk-shaped first damper member, a second damper member rotatable about an axis with respect to the first damper member, and at least one torsion elastic unit (torsion torsion).・ Spring unit, Torsionsfedere
inheit).

[0002]

2. Description of the Related Art Such a torsional vibration damping device is used, for example, in a clutch disk and makes it possible to attenuate torsional vibration generated in a power transmission path between an internal combustion engine and a driving wheel of a vehicle. FIG. 12 shows a clutch disk having a well-known torsional vibration damper. This known clutch disc 8s can be mounted, for example, on a clutch shaft (gear device input shaft) movably in the shaft longitudinal direction, but is fixedly connected to the clutch shaft for rotation about axis A. 10 s. The hub disk 1 has a hub disk 1
2s is fixed by, for example, welding. A driving disk 14s is arranged on one side of the hub disk 12s in the axial direction. The hub disk 12s
A cover plate 16s is arranged on the opposite side of the cover plate. The cover plate 16s is provided with a driving disk 14s.
And a plurality of pin elements 18s. In the radially (radially) inner region, the entraining disk 14s is rotationally fixed (without relative rotation) to the support ring 20s;
The support ring 20s is rotatably mounted on the hub 10s. A disc spring 22s is arranged between the hub disk 12s and the cover plate 16s. The disc spring axially prestresses the input of clutch disc 8s formed by entraining disc 14s and cover plate 16s, thereby supporting ring 20s
Abuts against the hub disk 12s under prestress, possibly with the intervention (intermediate mounting) of friction lining or the like. In the radially outer region, the entrainment disk 14
s is connected to the friction lining 24s. The friction lining can be sandwiched in a manner known per se for transmitting torque between the Anpressplatte of the motor vehicle clutch and the flywheel.

[0003] The hub disk 12s also has a carrying disk 14
s and the cover plate 16s are also provided with elastic windows (elastic body openings) 26s or 28s and 30s that extend in the circumferential direction, respectively. An elastic body 32s is arranged in the elastic body windows 26s, 28s, 30s. The elastic body 32s is connected to the control edge 3 of the hub disk 12s or the entraining disk 14s and the cover plate 16s by the ends located on opposite sides in the circumferential direction.
Contact 4s, 36s, 38s. The elastic body 32s prestresses the hub disk 12s to a predetermined rest position with respect to the entraining disk 14s and the cover plate 16s. When generating torque,
The elastic body is compressed, and as a result, the hub disk 12s
(Relative rotation) between the motor and the entraining disk 14s or the cover plate 16s may occur. Elastic body 32s
Cooperates in a manner known per se with the support ring 20s, which bears under prestress on the hub disk 12s, for damping torsional vibrations. Although it is not clear in FIG. 12, in the case of such a clutch disk, a plurality of elastic bodies are arranged successively in the circumferential direction in a correspondingly provided window.

In the case of such a torsional shock absorber, the elastic body is provided with a sufficiently large spring constant (elastic constant, spring constant, Federkonstante) in order to provide a suitable and predetermined damping characteristic (damping characteristic curve). On the other hand, there is a problem that the elastic body must have a sufficient elastic body length. However, if the length of the elastic body is too large, the elastic body tends to spread radially outward in the central region due to its prestress. In doing so, they contact the respective outer edges of the elastic windows in the hub disk or the entrainment disk and the cover disk, whereby, due to this contact, the friction in the so assembled torsional vibration damper becomes apparent. To be increased. Since this frictional force depends on the degree of compression of the elastic body, it provides a hard-to-calculate contribution to the frictional moment provided between the hub disk and the entrainment disk and the cover plate. Therefore it must be avoided.

From German Patent DE 34 31 809 a torsional vibration damper having an amplitude-dependent frictional moment is known. In the case of this known torsional vibration damper also, the hub disk is arranged axially between the driver disk and the cover plate. On the other hand, an elastic window is formed in each of the hub disk and the entrainment disk or the cover disk for receiving the elastic body. In particular, the elastic windows attached (correspondingly arranged) to one another in the hub disk and the entraining disk or the cover plate include:
Two elastic bodies that are respectively successive in the circumferential direction are arranged. Thereby, the elastic bodies form a torsion elastic body unit. On the other hand, the torsionally elastic unit so assembled rests, by its circumferentially spaced ends, against the control edge of the elastic window in the hub disk or the entrainment disk and the cover plate. An elastic contact arm of the intermediate disk is arranged between the mutually facing ends of the elastic. In order to provide an amplitude-dependent frictional moment, in the case of this known torsional vibration damper, on the one hand, a first friction device is provided which acts directly between the hub disk and the entraining or cover disk. .
On the other hand, a second friction device is provided, which works between the intermediate disk and the entrainment disk. Therefore, one of the two elastic bodies of the torsion elastic body unit is bridged and assisted by the second friction device depending on the torque transmission direction.

In the case of this known torsional vibration damper,
The torsion elastic units formed by both elastics are arranged along substantially their entire outer peripheral surface, especially on the basis of their prestress, outside the elastic window formed in the hub disk or the entraining disk and the cover plate. There is a problem of contact with the edge. This results in an additional frictional moment which is difficult to calculate in this known torsional vibration damper because of the prestressing of the torsional elastic unit in the torsional vibration damper, which occurs radially outwards. Cause inconvenience.

[0007]

SUMMARY OF THE INVENTION On the other hand, an object of the present invention is to provide a torsional vibration damping device for damping torsional vibrations in a power transmission system of an internal combustion engine, in particular for a clutch disk, to provide an unintended frictional moment. The object of the present invention is to provide a torsional vibration damping device capable of avoiding the occurrence of vibration.

[0008]

SUMMARY OF THE INVENTION According to a first aspect of the invention, the object is to provide a torsion damper for damping torsional vibrations in a power train of an internal combustion engine, in particular for a clutch disk, having the following arrangement. Solved by a vibration damper. That is, the torsional vibration damper comprises a disk-shaped first shock absorber member, a second shock absorber member rotatable about an axis with respect to the first shock absorber member, and at least one torsion elastic body unit. A torsion elastic device comprising: at least one elastic contact arm extending essentially radially with respect to the axis for the at least one torsion elastic unit; and At least one intermediate ring element rotatable about said axis with respect to the second damper member, wherein said at least one torsion elastic unit is essentially continuous in a circumferential direction one after the other. The torsion elastic body unit includes at least two elastic bodies arranged, and the end located on the opposite side in the circumferential direction of the torsion elastic body unit has a screw. Cooperate with the first damper member and the second damper member for vibration damping (the term "in response to" herein means a torsional vibration damper) During operation, i.e., during the transmission of torque from the internal combustion engine to the gear device via the torsional vibration damping device). A body contact arm is disposed circumferentially between mutually facing ends of the at least two elastic bodies of the at least one torsion elastic unit, and the at least one intermediate ring element includes the at least two intermediate ring elements; In order to prevent the elastic body from moving radially outward in an end region directed to said at least one elastic contact arm, And a means for preventing radial movement.

In the case of the torsional vibration damper according to the present invention, the torque between the first shock absorber member and the second shock absorber member is a torsional elastic body formed of at least two elastic bodies. Communicated by unit. This means that the torsional elastic unit has a clearly greater length with respect to known elastics which are often only formed in short lengths due to the aforementioned problems, and thereby has a more desirable damping characteristic Also can be given. However, due to the use of a plurality of relatively short elastic bodies which together form a torsional elastic body unit, the aforementioned problem, the escaping movement of the elastic body in the radially outward direction (movement, Ausweichbewegung) is essentially Can be avoided. This additionally has the effect that the elastics of the torsion elastic unit abut on the one hand the elastic contact arms of the intermediate ring element in their mutually opposing end regions and on the other hand radially by means of radial movement prevention means. Assisted by obstruction of the outward escape movement. That is, each of the elastic bodies of the torsion elastic body unit has an elastic body contact of the first shock absorber member, the second shock absorber member, or the intermediate ring element only in the region of the end on the opposite side in the circumferential direction. Contact the arm. Therefore, the outward retreating motion of each elastic body and the frictional force caused by contact with the first and / or second shock absorber members at that time are avoided.

According to a second aspect of the present invention, there is provided a torsional vibration damper for damping torsional vibration in a power transmission system of an internal combustion engine, particularly for a clutch disk, having the following configuration. That is, the torsional vibration damper comprises a disk-shaped first shock absorber member, a second shock absorber member rotatable about an axis with respect to the first shock absorber member, and at least one torsion elastic body unit. A torsion elastic device comprising: at least one elastic contact arm extending essentially radially with respect to the axis for the at least one torsion elastic unit; and At least two intermediate ring elements rotatable about the axis with respect to the second shock absorber member and with respect to each other, wherein the at least one torsion elastic unit is substantially circumferentially successive. And at least three elastic bodies arranged continuously in a row, and are opposite in the circumferential direction of the torsion elastic body unit. The end on the side is operatively associated with the first shock absorber member and the second shock absorber member for torsional vibration damping, and the elastic contact arm of the intermediate ring element, respectively, In the circumferential direction, at least one torsion elastic unit is arranged between the mutually facing ends of the successive elastic bodies.

In such a configuration of the torsional vibration damper according to the invention, the total elastic displacement (Gesamtfederweg) of each torsional elastic unit can be increased by providing more than two elastic bodies. However, this does not lead to a longer elastic body, but rather a relatively short elastic body with respect to each other with the interposition (intermediate mounting, intermediate support) of the elastic contact arm of each intermediate ring element. Supported. It is therefore also prevented that the elastic bodies are bulged too far radially outward in their central region due to the centrifugal forces generated during operation, thereby contacting other components.

In the case of such a configuration of the torsional vibration damper according to the invention, the respective intermediate ring element also has the advantage that the elastic body moves radially outward in the end region facing the respective elastic body contact arm. It may be taken into account to have further radial anti-motion means to prevent this.

In an embodiment of the invention, each intermediate ring element is arranged on the inner ring part radially inside the at least one torsion elastic unit or / and radially outside the at least one torsion elastic unit. And that the at least one elastic contact arm extends in a direction substantially radially away from the inner or outer ring portion.

[0014] The at least one elastic contact arm belonging to each intermediate ring element is advantageously provided at its circumferentially opposite end with a control edge for elastic contact. It is. In this case, the radial movement preventing means is formed by a projection which extends essentially circumferentially away from the at least one elastic contact arm in a radially outer end region of the control edge.

In order to ensure that the elastic force of the at least one torsion elastic unit is properly transmitted in a plane perpendicular to the axis, no tilting (tilting) moment is generated between the members. The first shock absorber member is provided with an elastic window for the at least one torsion elastic unit, and the second shock absorber member is provided with a corresponding elastic window for the at least one torsion elastic unit. An elastic window is provided,
At this time, the ends of the elastic windows in the first shock absorber member and the second shock absorber member located on the side opposite to the circumferential direction of the elastic window are respectively provided on the side opposite to the circumferential direction of the torsion elastic unit. A control edge for the contact of the located end is formed, and the at least one elastic contact arm of each intermediate ring element is provided in a radial part provided for elastic contact. It is proposed to lie in a common plane perpendicular to the axis, at least in the area of the axis, with the control edge formed in the elastic window of the second shock absorber element.

For example, each of the elastic contact arms is
In a region associated with the inner ring part and / or the outer ring part, the inner ring part and / or the outer ring part is axially offset with respect to said second damper member and is axially offset therefrom. It may take into account that it is bent so that it does not overlap in the direction.

At this time, the inner ring portion and / or
If the outer ring portion can be brought into contact with the axial side of the second shock absorber member, the respective ring portion cooperates with the second shock absorber member to prevent axial movement for the intermediate ring. Axial fixation is provided.

Each elastic contact arm is provided such that the entire radial extent of each elastic window in the second shock absorber member is available for contact between the respective elastic contact arm and the elastic. Is formed near the radially inner or outer end region of the elastic window in the second shock absorber member, respectively. By doing so,
Due to the bent area which is formed near the respective end area of the elastic window and which comes into contact with the shock-absorbing element during the radial movement of the respective elastic arm and thus of the intermediate ring element, A radial anti-motion device for the ring element is formed.

Furthermore, if it is taken into account that the radial extent of each intermediate ring element is smaller than the radial extent of the elastic window,
As little space as possible is required by the intermediate ring element, so that the structural space can be freed up for other components and the mutual interference between the intermediate ring element and another component can be avoided. That is guaranteed.

In particular, when a plurality of intermediate ring elements are provided, the bent area of the elastic contact arm of the first intermediate ring element is axially oriented with respect to the bent area of the elastic contact arm of another intermediate ring element. Is advantageously bent in the opposite direction. Then, in such a configuration, the respective inner or outer ring portion of the intermediate ring element is located axially on the opposite side with respect to the second shock absorber member. As a result, it is not possible for the intermediate ring elements to overlap one another and interfere with one another.

However, alternatively or additionally,
It is to be taken into account that the bent area of the elastic contact arm of the first intermediate ring element is bent in the same axial direction with respect to the bent area of the elastic contact arm of another intermediate ring element. it can. This is particularly advantageous when more than two, and thus for example three, intermediate ring elements are provided. In particular, the following can then be taken into account: That is, the radial extent of one of the intermediate ring elements is less than the radial extent of each of the other intermediate ring elements, so that the outer ring portion of the intermediate ring element with the smaller radial extent has a respective radial extent. Being located radially inward of the outer ring portion of another intermediate ring element, and / or being the inner ring portion of the intermediate ring element having the smaller radial extent, It is arranged radially outside of the inner ring part. This leads to a radial nesting (incorporation within one another, Ineinanderschachtelung) of the respective intermediate ring elements with curved areas bent to the same side. As a result, even when a plurality of intermediate ring elements, for example, three intermediate ring elements are provided, mutual interference cannot occur.

In order that the circumferential length (Umfangslaenge) of each torsion elastic body unit can be used very effectively, the following is proposed. That is, each intermediate ring element has only an outer ring portion, and each elastic contact arm has a wedge-shaped contact point that is essentially pointed radially inward.
l). In such a form, each elastic contact arm formed as a wedge-shaped contact portion is pointed in a radially inner region thereof. Because it does not have to be connected to the inner ring part. This means the following. In other words, it is possible to reduce the circumferential extent of each elastic contact arm, so that the control edges provided thereon are located relatively close to each other in the circumferential direction. As a result, more structural space is freed up for the elastics of each torsion elastic unit, and the effective (substantial) elastic length can thereby be longer.

It is proposed that the outer ring part be reinforced in such a configuration so that safe and fault-free operation can be ensured. It may take into account that each intermediate ring element comprises at least an inner ring part, and that the inner ring part is arranged axially adjacent to a radially inner region of the second shock absorber member. It is advantageous.

Each intermediate ring element can be bent axially from the inner ring part radially outward towards the second shock absorber member in the area of the at least one elastic contact arm. It is.
If the second shock-absorbing element is then configured to be essentially flat, the second shock-absorbing element can be stamped, for example, as a sheet or the like. In that case, no separate molding process is required.

Alternatively, a second shock absorber member is provided in a radial region corresponding to said at least one elastic contact arm, radially outwardly and axially towards said at least one intermediate ring element. It is possible to take into account that it is bent. Thereby, the contact point of the elastic body on the second shock absorber member or the elastic body contact arm, respectively, is even more desirable,
It can be repositioned into a common plane perpendicular to the axis.

Alternatively, however, the at least one intermediate ring element is designed to be essentially flat and the second shock-absorbing element has a radial direction in the radial region corresponding to the elastic contact arm. It may be bent axially outwards towards the intermediate ring element.

In order to be able to provide symmetrical torque transmission between the first and second shock absorber members, the first shock absorber member is axially second shock absorber. A first disc element arranged adjacent to the device member, and a region located axially opposite the first disc element with respect to the second shock absorber member and preferably radially outside; May have a second disk element fixedly connected to the first disk element. The inner ring part and / or the outer ring part of the respective intermediate ring element can then be axially aligned with the second shock absorber element and the first or second disk element of the first shock absorber element. It is located between. In such a configuration, an axial guide of the at least one intermediate ring element is provided at the same time.

Furthermore, the first disk element is rotatably connected to the support ring element in the radially inner region (ie, so as not to rotate relative to each other), and the at least one intermediate ring element has Wherein the inner ring portion is disposed between the first disk element and the second shock absorber member;
Can be taken into account.

The elasticity of the at least one torsion elastic unit, which is caused by the elastic body abutting on the at least one elastic contact arm or the radial movement preventing means and in the region of the elastic contact arm The at least one intermediate ring element is held centered with respect to the first damper element and the second damper element and the axis in normal operating conditions by means of a force diverting action (Federkraftumlenkungswirkung). However, the support ring element may be axially displaced in such a way that in the event of a malfunction, e.g. breakage of the elastic body, the at least one intermediate ring element is prevented from escaping aside. It is proposed to have a ring portion extending between one disk element and the second shock absorber member. The ring portion forms an emergency guide at its outer peripheral surface for the inner ring portion of the at least one intermediate ring element.

In order to provide a predetermined torsional vibration damping force,
It is possible for a friction device to be provided. The friction device acts to provide a torsional vibration damping frictional force between the second shock absorber member and the first shock absorber member.

At this time, for example, the support ring element
In some cases, with the intervention of the friction lining means, an elastic body device that abuts the second shock absorber member in the axial direction and is provided between the second shock absorber member and the second disk element. It is possible to prestress the support ring element towards the second shock absorber member. Instead, the second disk element
In some cases, the elastic device provided between the second shock absorber member and the support ring may be in contact with the second shock absorber member in the axial direction with the intervention of the friction lining means. One may take into account the prestressing of the second disk element towards the second shock absorber member.

In a particularly simple and inexpensive embodiment, the elastic device may comprise an elastic element formed by a disc spring (Tellerfeder), a ring spring (Ringfeder), a wave spring (Wellfeder) or the like.

In this case, the elastic element abuts the second shock-absorbing member in the region radially inward and the radially inward region of the second shock-absorbing member is provided by at least one axially directed projection. When fitted in the complementary void in, an additional predetermined frictional moment may be provided. This means the following. That is, the elastic element cannot rotate relative to the second shock absorber member, and when a torsional vibration occurs, a relative movement between the first shock absorber member and the second shock absorber member is made. The rotation imparts a predetermined frictional moment by frictional contact with the first shock absorber member.

A first shock absorber member and a second shock absorber member to prevent the elastic body of the at least one torsion elastic unit from being blocked, ie, compressed to its minimum length. It is proposed that a means for limiting the rotational displacement be provided in order to limit the rotational displacement between the two.

At this time, the rotation displacement limiting means may include a stopper means provided on the first shock absorber member and on the second shock absorber member and acting in the circumferential direction. The stopper means associated with the first shock absorber member may directly affect the stopper means associated with the second shock absorber member.

Instead, each intermediate ring element is provided with first stopper means cooperating with stopper means associated with the first shock absorber member,
It can also be taken into account that a second stopper means is provided which cooperates with a stopper means associated with the second shock absorber member and / or with a separate intermediate ring element. This is particularly advantageous when the elastic bodies of the at least one torsion elastic unit have different spring constants. In such a case, a graded (gradual) elastic force may be provided by the torsion elastic unit.

In this case, it is possible, for example, for the first and second stopper means to be formed on the respective intermediate ring element by substantially radially directed stopper surfaces. The stopper surface is formed on a protrusion extending in a direction away from the at least one elastic body contact arm in a circumferential direction.

In a particularly simple form, it is proposed that the stop means associated with the first shock-absorbing element is formed by at least one pin element which connects the first disk element with the second disk element. . Thereby, the use of additional members for forming the stopper can be avoided.

The stopper means associated with the second shock absorber member may be formed by a substantially radially extending stop surface provided in a region radially outside the shock absorber member.

[0040] The plurality of elastic bodies of the at least one torsion elastic body unit may have the same spring constant. However, alternatively, the plurality of elastic bodies of the at least one torsion elastic body unit may have different spring constants. Thereby,
As described above, a stepwise elastic behavior of the at least one torsion elastic unit may be obtained.

In modern motor vehicle construction, flywheels, clutch discs, pressing plate assemblies (assemblies),
And a clutch unit comprising a clutch casing are often pre-assembled, manufactured and sold. In such a clutch unit, a screw pin (stud) penetrating the flywheel must be attached to the end face of the crankshaft. An elastic body in the second shock absorber member, in order to enable the incorporation of a screw through the flywheel by such a clutch unit, which can have the torsional vibration damper according to the invention, for example as a clutch disc Wherein the window has a greater radial extent inward than the corresponding elastic windows in the first and second disc members of the first shock absorber member, in the first and second disc members,
An axial passage opening (Axialdurchgangsoe) aligned in the axial direction is provided in a region corresponding to a radially inwardly extending portion of the elastic window in the second shock absorber member.
ffnungen) is proposed. This is particularly advantageous in connection with the torsional vibration damper according to the invention. Because of the configuration of the at least one torsion elastic unit having a short elastic body, it is possible that the at least one torsion elastic unit is moved radially inward and thereby crank the flywheel. This is because it is possible to reach a radial area where a screw pin for fixing to the shaft is provided.

The torsional vibration damping device according to the present invention can be assembled as follows. That is, the first or second shock absorber member includes an input portion of the clutch disk, particularly the entrainment disk, and the other member includes an output portion of the clutch disk, particularly the hub disk.

In a form which can be manufactured simply and inexpensively, the parts forming the output of the first and second shock absorber members are fixedly connected to the hub, preferably by welding or the like. Can be taken into account. In this case, the support ring may be further mounted on the hub so as to be rotatable around the axis.

According to a third aspect of the present invention, there is provided a torsional vibration damper having the following structure for damping torsional vibration in a power transmission system of an internal combustion engine, particularly for a clutch disk. That is, the torsional vibration damper comprises a disk-shaped first shock absorber member, a second shock absorber member rotatable about an axis with respect to the first shock absorber member, and at least one torsion elastic body unit. And at least one elastic contact arm extending essentially radially with respect to the axis for the at least one torsion elastic unit, and the first damper A device member and at least one intermediate ring element rotatable about the axis with respect to the second shock absorber member, wherein the at least one torsion elastic unit is substantially circumferentially successive. And at least two elastic bodies that are arranged continuously, and are located on opposite sides in the circumferential direction of the torsion elastic body unit. The end is operatively associated with the first shock absorber member and the second shock absorber member for damping torsional vibrations, and the at least one elastic contact arm circumferentially extends the at least one torsional elastic body. A first shock absorber member, which is arranged between the opposite ends of the at least two elastic bodies of the unit and is in the form of a disc, has a first disc element and a first disc element with respect to the first disc element. A second disk element spaced axially and fixedly connected thereto, said second shock-absorbing member being essentially disk-shaped and axially At least one intermediate ring element is disposed between the first disk element and the second disk element. Both, in the region of the elastic body contact arms for each of the torsion spring member unit, located approximately perpendicular common plane relative to the axis together with the second shock absorber element.

In the case of such a configuration, the force transmission between the second shock absorber member and the elastic contact arms of the respective intermediate ring elements attached to the respective torsion elastic units is performed with respect to the axis. It is ensured that the occurrence of a tilting (tilting) moment in the respective torsional elastic unit is sufficiently prevented because of the small space requirements in the axial direction.

If each intermediate ring element is formed only by one disk element, a torsional vibration damper can be obtained which is particularly simple to assemble and requires little axial structural space.

Advantageously, the number of intermediate ring elements rotatable with respect to each other is one less than the number of elastic bodies of each torsion elastic unit, and then each intermediate ring element has its own torsion element. The elastic unit has one elastic contact arm. The number of interfaces formed between the elastics of one torsion elastic unit is one less than the number of each elastic, so that exactly one intermediate ring element is attached for each interface It is provided with an elastic contact arm. Thereby, the number of members can be kept as low as possible by providing more than two elastics for each torsion elastic unit.

[0048]

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be described in more detail hereinafter with reference to the accompanying drawings, in which: FIG. FIG. 1 is a sectional view of a clutch disk 8 having a torsional vibration damping device (torsional vibration damper) according to the present invention.
The clutch disk 8 has a hub 10. The hub is, for example, a transmission input shaft (clutch shaft, Getr
iebeeingangswelle) (not shown), is movable in the longitudinal direction of the axis A, but is rotatably mounted on the input shaft. For this purpose, the hub 10 has teeth 11 on the inner peripheral surface. The hub 10 and the hub disk 12 are fixedly connected to each other (that is, not to rotate relative to each other). The hub disk 12 may be coupled to the hub 10 in a region radially inward thereof, for example by welding or the like. Hub disk 1
2 consists of only one part which can be produced, for example, by stamping.

In the direction of the axis A, the hub disk 12
On one side of this is arranged an entraining disk (Mitnehmerscheibe) 14. The entraining disk 14 is rotationally fixedly connected to a support ring (bearing ring) 20 in a radially inner region. On the other hand, the support ring 20 is rotatably arranged on the hub 10. In the radially outer region, the entrainment disk 14 is fixedly connected to the friction lining 24. The friction lining can be clamped between the corresponding friction linings of a clutch which is arranged on a flywheel or a pressing plate (not shown). Thus, by tightening the friction lining 24 between the flywheel and the pressing plate, a rotationally fixed connection of the clutch disc 8 with the flywheel and thereby with the crankshaft of the mechanical device can be created.

A cover plate (Deckblech) 16 is arranged on the side opposite to the entraining disk 14 with respect to the hub disk 12 in the direction of the axis A. The cover plate 16 has, in its radially (radially) outer region,
It is fixedly connected to the entraining disk 14 by a plurality of pins (bolts) arranged in a circumferential direction. In the radially inner area, the cover plate 16 is
Seven. As a result, it forms a radial spacing with respect to the outer peripheral surface of the hub 10.

Elastic windows (elastic opening) 26, 28, or 30 are arranged on the hub disk 12, the entraining disk 14, and the cover plate 16, respectively (FIGS. 2, 3, and 5). See also). Elastic bodies (eg, springs) 32, 40 are disposed in the elastic windows 26, 28, 30, as described in more detail below. The elastic body forms a torsion elastic body unit (torsion spring unit) 33, and the hub disk 12 and the entraining disk 14 and the cover plate 1
6 (ie, between the hub disk 12 and the entrainment disk 14 and between the hub disk 12 and the cover plate 1).
6). As can be seen in FIGS. 2, 3, and 5, the hub disk 12
Or, in the entraining disk 14 and the cover plate 16,
Three elastic windows 2 that are continuous in a row in the circumferential direction
6, 28, 30 are provided for receiving the elastic bodies 32, 40. This results in a symmetric dispersion of the force action (dynamic effect, Kraftwirkung) of the elastic bodies 32, 40 about the axis A.

Hub disk 12 or entrainment disk 14
Window 2 on cover plate 16
Each of 6, 28, 30 has a control edge (Steuerkanten) 34, 36, or 38 at its opposite end in the circumferential direction for abutment (contact) of the elastics 32, 40, respectively. .

As can be seen in FIGS. 1 and 3, there is further provided an intermediate ring (Zwischenring) 42 which is shown in detail in FIGS. 4a and 4b. Intermediate ring 4
2 is extended only axially between the hub disk 12 and the entraining disk 14 by a radially (radially) inner part 44. In the central or curved region 46, the intermediate ring 42 is bent radially outwards towards the hub disk 12. At that time, in the radially outer region 48, the intermediate ring 42 is attached to the elastic window 2 of the hub disk 12 in the axial direction.
6, each extending radially outward (i.e., the radially outer region lies flush with the hub disk). As can be seen in particular in FIG. 4 a, the intermediate ring 42 is formed by an inner ring part 50 as well as an outer ring part 52, in the embodiment shown three elastic contact arms (Federanlagearme) 54 therebetween. Extend. In particular, the curved portions of the intermediate ring 42 each
The elastic body contact arm 54 is provided in a radially central region. The intermediate ring 42 is essentially freely rotatable about the axis A with respect to the hub disk 12 or the entraining disk 14 and the cover plate 16.

An elastic window 59 in the intermediate ring 42 is formed between the elastic contact arms 54 in succession in the circumferential direction. The elastic windows are used for receiving elastic bodies 32 and 40, respectively, as described below.

As can be seen especially in FIG. 3, the intermediate ring 42 is arranged as follows with respect to the hub disk 12. That is, the elastic contact arm 54 of the intermediate ring 42 extends in the circumferential direction substantially in the central region of the elastic window 26 in the hub disk 12. The elastic windows 28, 30 in the entrainment disk 14 or the cover plate 16 are arranged circumferentially in alignment with the elastic windows 26 in the hub disk 12, so that the elastic contact arms 54 of the intermediate ring 42
Extends similarly in the circumferential direction to the central region with respect to the elastic windows 28, 30 in the entraining disk 14 or the cover plate 16. Elastic contact arm 54
Have respective control edges 58 in the end regions on opposite sides in the circumferential direction. The elastic body 32 or 40 can abut on the control edge by its ends. As can be seen in particular in FIG. 3, in this embodiment, each of the elastic bodies 32, 40 has one of its ends, the hub disk 12, the entraining disk 14,
Or the control edges 34, 36, 3 of the cover plate 16
8 and a control edge 58 of the intermediate ring 42 by the other end, respectively.

Further, the hub disk 12, the intermediate ring 4
2, and the entrainment disk 14 or the cover plate 16 has a rotational displacement limit between the hub disk 12 and the entrainment disk 14 or the cover plate 16 (Drehweggrenzung).
Are provided with respective stopper means. The stopper means includes a stop surface 60 provided on the hub disk 12 in a region radially outward of the control edge 34 of the hub disk. The stopper surface is provided on a protrusion 62 extending in the circumferential direction of the hub disk. Correspondingly, a stop surface 66 is formed on the projection 64, which extends circumferentially and forms part of the outer ring portion 52, radially outward of the control edge 58 of the intermediate ring 42, respectively. The stop surface is positioned for cooperation with the stop surface 60 on the hub disk 12. Similarly, a stopper surface 68 is formed on the protrusion 64 extending in the circumferential direction from the elastic body contact arm 54. The stopper surface 68 is oriented in the circumferential direction opposite to the provided stopper surface 66, and one circumferentially extending recess 70 is provided between the pin 1 and the stopper surface 66.
8 for one. By means of the pins, the entraining disk 14 is fixedly connected to the cover plate 16. Although only one such pin 18 is shown in FIG. 3, of course, one such pin may be provided at each recess 70.

Further, in the case of the clutch disk 8,
A friction device 74 that contributes to damping the torsional vibration is provided. As can be seen in FIG. 1, the friction device 74 comprises a support ring 20 and a disc spring 76.
including. A disc spring 76 is arranged on the opposite side of the hub disk 12 with respect to the support ring 20 in the configuration shown in FIG. Works. As a result, the entraining disk 14 is axially prestressed by the disc spring 76 via the support ring 20.
ng) against the hub disk 12. In doing so, a corresponding frictional force is generated. On the one hand the support ring 20 and / or on the other hand the hub disc 1
By providing a friction lining or a friction element on 2, it is possible to adjust in a suitable manner the frictional force generated between the support ring 20 and the hub disk 12. It will be obvious to those skilled in the art that the friction device 74 can be assembled in various ways.

The inner ring part 50 arranged between the entraining disk 14 and the hub disk 12 in the axial direction
Is radially opposed to a portion of the support ring 20 located between the entrainment disk 14 and the hub disk 12. The emergency guide is thus provided by the support ring 20 in its radially inner region for the intermediate ring 42.
(Notfuehrung). Due to the circumferentially arranged torsion elastic units, the intermediate ring 42, when functioning normally, is centered about the axis A (ie,
In this normal state, the inner ring portion 50 and the support ring 2
No contact between 0 and 0 occurs. However, when a malfunction (Fehlfunktion) occurs in one of the elastic units, this leads to an asymmetric radial force action on the intermediate ring 42, and the radial movement of the intermediate ring accordingly. Can occur. However, in this case, such radial movement is prevented due to the emergency guide provided by the support ring 20.

The functioning method (action) of the torsional vibration damping device according to the present invention will now be described with particular reference to FIGS. FIG. 3 shows the intermediate ring 42 with respect to the hub disk 12 or the entraining disk 14 and the cover plate 16.
FIG. 4 is a diagram illustrating the neutral position, that is, the no-load position. For example, in the process of meshing the clutch (ie, engaging the clutch), between the driving disk 14 and the cover plate and the hub disk 12 (that is, between the driving disk 14 and the hub disk 12 and between the cover plate and the hub disk 12). When a torque effect occurs, this leads to a relative rotation (torsion) of the entrainment disk 14 and the cover plate 16 in the circumferential direction with respect to the hub disk 12. At that time, the elastic bodies 32 and 40
Compressed due to abutment of control edges 34, 36, 38. In the following, the elastic bodies 32 and 40 have different spring constants (elastic constant, spring constant), for example,
Assume that elastic 32 has a smaller spring constant. At that time, when the elastic bodies 32 and 40 are connected in series due to the increase in the torque action, the elastic body with the smaller spring constant is firstly compressed more strongly. That is, the elastic body 40 remains almost in its starting state (initial state), whereas the elastic body 32 first contacts the stopper surface 60 or 66 belonging to the hub disk 12 or the intermediate ring 42 until they come into contact with each other. Compressed. At this time, in order to prevent the elastic body from being damaged, the elastic body 32 is not yet in a blocked state at the time of such mutual contact of the stopper surfaces 60 and 66, that is, the elastic body 32 is not yet completely compressed. The configuration has been chosen not to be. If the torque continues to increase at that time, the second elastic body 40 is also compressed. At that time, in some cases, the compression is performed until the stopper surface 68 contacts the pin 18. Also, at this time, in this configuration, the elastic body 40 is not yet in the blocked state at the time of such mutual contact between the stopper surface 68 and the pin 18. In this state where the stop surface and the pin are in contact, subsequent rotation between the hub disk 12 and the entraining disk 14 or the cover plate 16 is no longer possible. During this relative rotation between the hub disc 12 and the entraining disc 14 or the cover plate 16, a stepwise elastic force action is provided because the elastic body 32 or 40 is provided with a different spring constant. This elastic action results in a corresponding stepwise torsional vibration damping. A corresponding stepwise elastic force action occurs when the elastic bodies 32, 40 relax. At that time, first, the elastic body having the larger spring constant, that is, the elastic body 40 relaxes, and then the elastic body 32 relaxes only after that. The friction device 74 leads to appropriately damping the generated torsional vibration.

Due to the torsional vibration damping device according to the present invention, despite the use of the short elastic members 32 and 40, a relatively long member generally having a length substantially corresponding to the entire length of the elastic members 32 and 40 together. The use of an elastic body provides a damping action that can be obtained. This means that the overall length of the elastic body together with the length of the relatively long elastic body corresponds to the relatively long elastic damping displacement (Federdaempf
ungsweg). Nevertheless, due to the use of the short elastic bodies 32, 40, the elastic bodies escape radially outward in their central region due to their prestress, and the hub disk 12 or the entraining disk 14 and the cover plate 16, It is prevented that the respective elastic windows are restricted from contacting radially outward portions (that is, portions defining radially outward portions of the respective elastic windows). Thus, additional frictional contact of the elastic body can be avoided. Thereby, a predetermined torsional vibration damping state can be generated. As can be seen especially in FIG.
, And on the other hand the associated control edges 34, 36, 38 belonging to the hub disk 12 and the entraining disk 14 or the cover plate 16, respectively.
Are arranged to extend substantially parallel to each other. As a result, the elastic body 32 or 40 compressed between the control edges 58 or 34, 36, 38 facing each other in the circumferential direction is compressed substantially linearly. Such a posture arrangement of the respective control edges with respect to each other (Lag
This is possible by making the elastics located between the control edges relatively short, and thus by making the circumferential distance of the control edges relatively short from one another. Such relative positioning of the control edges with respect to each other also contributes to preventing the avoidance behavior (escape) of the elastic body that deviates from the elastic body longitudinal axis.

To prevent escape of the elastics 32, 40 in the area where they abut the corresponding elastic contact arm 54 of the intermediate ring 52, stopper surfaces 66, 68
The circumferential projection 64 also has a radial (radial) movement preventing means for the elastic bodies 32, 40. Thereby, on the one hand only to the hub disk 12 or the entraining disk 14 and the cover plate 16 on their opposite end regions, on the other hand to the intermediate ring 42
Contact is guaranteed. The elastic bodies 32, 40 do not contact the radially outer regions of the hub disk 12 or the entraining disk 14 and the cover plate 16 in their central region in the circumferential direction. Thereby, the intermediate ring 42 is resilient in the area of its elastic contact arm 54 (elastic redirection, Fede).
rkraftumlenkung). That leads to the advantages mentioned above.

In FIG. 3, only one of the elastic windows 26 of the hub disk 12 has elastic members (for example, springs) 32 and 4.
Although 0 is illustrated, it is a matter of course that another elastic window 26 should be provided with such an elastic body.
Further, an elastic body (e.g., a spring) having the same spring constant for the elastic bodies 32 and 40 may be used. At this time, a damping behavior substantially corresponding to the damping behavior of one elastic body having a total length substantially equivalent to the sum of the lengths of the two elastic bodies 32 and 40 is also obtained.

Furthermore, the intermediate ring 42 is omitted in the region between the circumferential projection 64 where it merely has the inner ring part 50 and the outer ring part 52 has the respective stop surfaces 66 and 68. Alternatively, it may be assembled. This leads to relatively light components that can be manufactured relatively inexpensively. Further, the rotational displacement limiting means may act directly between the hub disk 12 and the entraining disk 14 or the cover plate 16 without the intervention of the intermediate ring 42.

Next, another embodiment of the torsional vibration damper according to the present invention will be described with reference to FIG. Members corresponding to those previously shown and described with respect to FIGS. 1 through 6 are designated with the same reference numeral followed by "a".
The structure of the embodiment shown in FIG. 7 essentially corresponds to the structure of the embodiment shown in FIGS. Thus, only the differences are addressed. In particular, in the case of the embodiment shown in FIG. 7, the elastic window 26a in the hub disk 12 is formed as follows. That is, the elastic body window does not end immediately inward in the radial direction of the elastic body 32a but spreads further inward in the radial direction. Then, in the corresponding radial area, the through-holes 80a, 8
2a is formed. Accordingly, the elastic window 26 extended inward in the radial direction of the hub disk 12a.
a and the through-holes 80a and 82a in the entraining disk 14a and the cover plate 16a form a through-hole 84a extending in the axial direction. The through-hole 84a
Are further aligned with the respective elastic windows in the intermediate ring. In that case, the entraining disk 14a and the cover plate 16a form an elastic guide or support in the region radially inside the elastic window. In modern vehicle constructions, especially motor vehicle clutches, are often supplied as pre-assembled assemblies. In that assembly, the flywheel, clutch casing, pressing plate assembly, and clutch disc are already assembled. In that case, such a clutch unit must also be fixed to the crankshaft of the internal combustion engine. This can be done, for example, by screw pins (studs) passing through the flywheel. In the case of the assembled clutch unit, too, it extends axially into the clutch casing or the pressing plate assembly (not shown), on the one hand, in order to obtain a passage (Zugang) for threading the screw pin through the flywheel. Through holes are provided. On the other hand, in order to allow an unobstructed penetration of the screw pin, a through hole 84a is provided in the clutch disc 8a, as shown in FIG.
The number of through holes 84a provided in the circumferential direction can be selected corresponding to the through holes provided in each flywheel for the screw pins.

Here, it is described that the through-hole 84a is provided in connection with the torsional vibration damper assembled in accordance with the present invention. It is obvious to those skilled in the art that such a through-hole 84a can be provided and that providing such a through-hole has an independent and protective ability viewpoint (ie, an important invention per se). .

Next, another embodiment of the torsional vibration damper according to the present invention will be described with reference to FIGS. Members corresponding to those shown in FIGS. 1-6 are described and illustrated with the same reference numerals followed by "b", "c", "d", or "e".

The structure of the torsional vibration damper of FIG. 8 essentially corresponds to the structure shown in FIGS. However, as can be seen in FIG. 8, the disc spring 76b has a hub disk 1 in its radially (radially) inner region.
2b, and is configured to contact the cover plate 16b in a radially outer region thereof. In its radially inner area, a disc spring 76b is provided with an axial projection 8
6b, and the axial protruding portion 86b is
2b fits into the corresponding recess 88b. These recesses 88b in the hub disk 12b are, for example,
It can already be provided at the time of punching (die-cutting) the hub disk 12b from the thin plate member. This forms a rotationally fixed connection between the hub disk 12b and the disc spring 76b. This allows, on the one hand, the frictional contact during relative rotation between the hub disk 12b and the entraining disk 14b or the cover plate 16b to the hub disk 12b, possibly with the intervention of friction means (intermediate support). On the other hand, and, on the other hand, a disc spring 76b and a cover plate 1 which are rotationally fixedly connected to the hub disk 12b.
6b is provided. The required damping moment can then be adjusted appropriately by means of a suitable material selection (metal, synthetic (eg plastic), etc.) of the friction lining of the disc spring 76b or the support ring 20b or possibly provided. Although not shown in FIG. 8, the disc spring 76b is still rotatably connected to the cover plate 16b in a corresponding manner, so that a frictional contact is created between the disc spring 76b and the hub disc 12b. You may. In addition, the disc spring 76
b may be supported on a rotatable member in this regard with the aid of a thrust washer or the like.
Thereby, the friction moment is additionally influenced on the basis of the material selection (metal, synthetic material, etc.) of the thrust washer. In addition, the disc spring 76b can be bent or suitably shaped in the area abutting the rotatable member in this regard. Thereby, the frictional force provided by the disc spring 76b can be adjusted.

In the embodiment shown in FIG. 9, the inner ring portion 50c of the intermediate ring 42c is
2c and the cover plate 16c. The entraining disc 14c is moved by the support ring 20
c, again in the direction of the hub disk 12c, possibly with the intervention of friction linings or suitable friction means (in other words, the cover plate 16c is prestressed by a disc spring). Stressed, thereby causing the entrainment disk 1
4c and support ring 20c are pulled toward hub disk 12c). This embodiment has the following advantages over the embodiments shown in FIGS. In other words, in the case of the embodiment shown in FIGS. 1 to 8, when the friction lining provided between the support ring and the hub disk or the wear (wear) of the support ring itself occurs, it is associated with the wear. During the axial movement of the entrainment disk towards the hub disk, the intermediate ring is clamped between the entrainment disk and the hub disk in the region of its inner ring part, whereby its free relative rotation is possible Sex can be lost. This is avoided in the case of the embodiment shown in FIG. Because, hub disk 1
This is because, in the event of wear in the area of contact of the support ring 20c with 2c, tightening of the intermediate ring 42c cannot take place in the area of its inner ring part 50c.

In the embodiments shown in FIGS. 1 to 9, the hub disks 12 are formed as follows. That is, it is flat and instead the intermediate ring is bent in the central region. This means that it is possible to use conventional members for the hub disk,
This has the advantage that the component can be connected to the hub by welding or the like in a manner known per se. Due to the flat design of the hub disk, changes in its bent area are avoided during welding of the hub disk to the hub and in the event of high temperatures at the hub disk. Also, the hardness of the hub disk is not necessary after it has been bent and possibly welded to the hub.

In the embodiment shown in FIG.
Both d and the intermediate ring 42d are bent towards each other in their radially central region where the elastic window is provided. This means that the contact point of the intermediate ring 42d in the region of the elastic contact arm 54d with the elastic and the control edge 3 of the hub disk 12d on the elastic.
This leads to the advantage that the contact points of the hub disc in the region of 4d can be arranged in the axial direction with more desirable symmetry with respect to the central axis of the elastic body. As a result, the axially oriented force component and the tilting (tilting) moment of the elastic body can be avoided.
In order to apply a prestress toward the hub disk 12d via the support ring 20d to the entraining disk 14d, in the configuration shown in FIG. 10, a wave spring (Wellfeder) 90d is used.
Is provided. However, it is obvious that for all embodiments of the invention, another suitable elastic or elastic device may be used instead of the illustrated disc spring or the illustrated wave spring.

In the embodiment shown in FIG. 11, an intermediate ring 42e which is formed essentially flat is provided. Then, in this configuration, the hub disk 12e is bent axially towards the intermediate ring 42e in the region of its control edge 34e. In the case of this form, the elastic body 76
e is disposed between the hub disk 12e and the support ring 20e. As a result, the support ring 20e with the entraining disk 14e is pushed away from the hub disk 12e. In doing so, the cover plate 16e further comes into contact with the hub disk 12e, thereby generating the necessary frictional moment for damping the torsional vibration. Although not shown in FIG. 11, a friction lining or a suitable friction device is again provided between the cover plate 16e and the hub disk 12e so that a friction force suitable for each requirement can be provided. You may.

In the case of the embodiment shown in FIG. 11, the following can be taken into consideration. In other words, when the wear occurs in the area of friction lining or in the area of contact between the cover plate 16e and the hub disk 12e, the intermediate ring 4
2e tightening is avoided. This is because the inner ring portion 50e is disposed axially between the entraining disk 14e and the hub disk 12e, and the entraining disk 14e is pushed away from the hub disk 12e by the elastic body 76e when wear occurs. It is.

FIGS. 13 to 15 show another embodiment of the torsional vibration damping device according to the present invention. FIG.
6 correspond to those in the embodiment described with reference to FIG. 6 with the same reference numerals followed by “f”. In particular, FIGS. 13 to 15 show the torsional vibration damping device according to the invention in connection with a two-piece flywheel (ie, a two-mass flywheel). At this time, the two flywheels are, for example, a main thin plate (Pri) fixedly attached to the motor output shaft 100f.
maerblech) 102f and a cover plate 16f fixedly connected to the main thin plate 102f and axially spaced therefrom. In particular, the cover plate 16f is fixedly connected to the main thin plate 102f in a radially inner region by pins 104f. The main thin plate 102f is further moved by the pin to the motor output shaft 10f.
0f. In the radially outer area,
The cover plate 16f is fixed to the main thin plate 10 by pins 18f.
It is fixedly connected to 2f.

On the other hand, a hub disk 12f is provided between the main thin plate 102f and the cover plate 16f.
It is rotatably mounted with respect to 2f and the cover plate 16f. In the region outside in the radial direction, the main thin plate 10
2f is fixedly connected to the first flywheel mass portion 106f by a pin 108f. On the other hand, the hub disk 12f has a pin 112 in its radially outer region.
It is fixedly connected to the second flywheel mass part 110f by f.

The hub disk 12f, the main thin plate 102f and the cover plate 16f are also provided with three elastic windows 26f, 28f and 30f, which in this case also continue one after the other in the circumferential direction. Each of these elastic windows is a torsion elastic unit 3
3 is used for acceptance. As can be seen particularly in FIG. 13, the elastic windows 26f, 28f, 30f are respectively formed as follows. That is, these may be provided with three elastic bodies that follow each other successively in the circumferential direction (only one elastic body (spring) 32f of the torsion elastic body unit 33 is shown in FIGS. 13 and 14). ing).

Further, the torsional vibration damping device includes two intermediate rings 42f and 42f '. Each of the intermediate rings 42f, 42f 'has an elastic contact arm 54f or 54f' for a respective torsion elastic unit 33. As can be seen particularly in FIG. 14, the elastic contact arms 54f, 54f '
Are arranged so as to extend in common with the hub disk 12f on a plane perpendicular to the hub disk (that is, to be located on a common plane with the hub disk). The elastic contact arms 54f, 54f 'are bent as follows at their radial end regions, which are located near the radial end regions of the elastic windows 26f of the hub disk 12f, respectively. That is, the inner ring portion 50f and the outer ring portion 52f of the intermediate ring 42f are arranged on the left side of the hub disk 12f in the axial direction in FIG. 14, and the corresponding inner and outer ring portions 50f 'and 50f' of the intermediate ring 42f ' 52f 'is disposed on the right side of the hub disk 12f in FIG. Thereby, both intermediate rings 42f, 42f 'are rotatable relative to each other, and there is no mutual interference between the inner and outer ring portions of the different intermediate rings, respectively.

FIG. 23 shows a mechanical equivalent circuit diagram of such a torsional vibration damping device having three torsion elastic body units 33. The torsion elastic body unit includes three elastic bodies (for example, springs) 32f, 4f,
0f and 114f. Torsion elastic unit 3
3, both intermediate rings 42f, 42f
The main thin plate 102f or the cover plate 16f is directly connected by the elastic bodies 32f, 40f, 114f connected in series with the elastic body contact arms 54f, 54f 'of f' interposed therebetween.
And the hub disk 12f provide torsional vibration damping.

The functioning method (operation) of the torsional vibration damper thus assembled substantially corresponds to the functioning method described above with reference to FIGS. Therefore, a detailed description will not be given here.

Also, in the case of the torsional vibration damper shown in FIGS. 13 to 15, a rotation displacement limiting device is provided between the hub disk 12f and the main thin plate 102f or the cover plate 16f. 13 and 14
As can be seen in, the hub disk 12f has three connecting portions 116f that extend radially outward. The connecting part is a second flywheel mass part 11
It is used for connecting the hub disk 12f to the hub disk 12f. The three connecting portions 116f have an angular spacing of 120 ° with respect to each other. Correspondingly, the main thin plate 102
f and the cover plate 16f are 120 ° with respect to each other.
Are connected by three pins 18f arranged at an angular interval of. Hub disk 12f and main thin plate 102f
Or, when relative rotation with the cover plate 16f occurs, when a predetermined rotation angle (60 ° in this embodiment) is exceeded, the connecting portions 116f are brought into contact with the respective pins 18f, thereby further rotating. Hinder. In this case, in particular, the elastic bodies 32f, 40f and 114f of the torsion elastic unit 33 are not yet in the blocking state at the time of mutual contact between the connecting portion 116f and the pin 18f, that is, they are still compressed to the maximum. Not configured. Of course, different types of rotational displacement limiting means may be provided in a corresponding manner. For example, first rotational displacement limiting means for limiting the relative rotation between the hub disk and the intermediate ring 42f;
f ', and third rotational displacement limiting means for limiting the rotational displacement between the intermediate ring 42f' and the main thin plate 102f and the cover plate 16f. What is provided can be taken into account. On the other hand, in the case of such a configuration, it is possible to consider elastic bodies having different spring constants as the three elastic bodies of each torsion elastic body unit 33. As a result, a gradual damping behavior can again be provided in this case.

As can be seen particularly in FIG. 14, the intermediate rings 42f and 42f 'are prevented from both radial and axial movement. Elastic contact arms 54f, 54
f ′ are bent near the radial ends of the elastic windows 26f, respectively.
(Radialsicherung). As a result, the elastic contact arms each have an elastic window 26f due to their bent regions during radial movement.
Contact the radial end face of The axial fixing portion is provided by the inner and outer ring portions 50f, 52f of the intermediate ring 42f being held between the hub disk 12f and the main thin plate 102f. Correspondingly, the intermediate ring 42f 'or its inner and outer ring portions 50
f 'and 52f' are axially held between the hub disk 12f and the cover plate 16f.

On the other hand, the hub disk 12f and the main thin plate 1
A conventional friction device 74f is provided to provide vibration damping between the cover member 02f and the cover plate 16f. The friction device 74f includes a first friction ring 120f.
As well as the second friction ring 122f. The hub disk 12f is axially supported in the radially inner region of the main thin plate 102f by the first friction ring, and is likewise guided radially. The second friction ring is a hub disc 1
It is arranged between 2f and the disc spring 76f. The hub disk 12f is prestressed toward the main thin plate 102f by the disc spring. The disc spring 76f is provided with an additional portion 86f extending in the axial direction.
The appendage cuts into a corresponding cavity in the cover plate 16f, thereby providing a rotationally fixed connection between the disc spring 76f and the cover plate 16f. Further, it is obvious to those skilled in the art that the friction device 74f can be configured in various shapes adapted to the specific requirements.

FIG. 16 shows the torsional vibration damper shown in FIGS. 13 to 15 in connection with a clutch disk. The torsional vibration damper shown in FIG.
In function and structure, it corresponds to the torsional vibration damper shown in FIGS. Thus, in this regard, see the previous embodiment. The same or corresponding members are denoted by the same reference numerals in FIGS. 13 to 15 and FIG. In the case of the torsional vibration damper of FIG. 16, the main thin plate 102f is used as the entrainment disk, and the friction lining 24f of the clutch disk is attached to the radially outer region by a pin 108f. It can then be clamped for torque transmission between the corresponding friction lining of the flywheel and the pressing plate. Hub disk 1
2f is fixedly connected to the hub 10f in its radially inner region. The hub has inner teeth 11f, whereby it is connected so as not to rotate relative to the clutch shaft, but movably in the axial direction.

FIGS. 17 and 18 show another alternative form of the intermediate ring 42g. The intermediate ring 42g is
It simply has an outer ring portion 52g. At this time, the elastic body contact arm 54g extends radially inward from the outer ring portion. At this time, as can be seen particularly in FIG. 17, the elastic contact arm 54g is mainly composed of a wedge-shaped contact portion.
(Anlagekeile). The wedge-shaped contact point is pointed inward in the radial direction. as a result,
Each control edge 58g intersects at the inner vertex. In such a configuration, both control edges 58g of the respective elastic contact arm 54g are arranged closer to each other in the circumferential direction than in the embodiment shown in FIGS. 1 to 6, for example. I have. This has the advantage that if the lengths of the elastic windows in the circumferential direction are equal, more elastic volume (Federvolumen) is free (where the elastic volume is larger, It also means that the ratio of diameter, ratio of length, and elasticity are greater). As a result, the damping characteristic (damping characteristic curve) of a torsional vibration damping device having one such intermediate ring or a plurality of such intermediate rings has a very long elastic body. It is even more assimilated to the damping behavior of the torsional vibration damper thus configured (a
ngleichen) get. Nevertheless, the elastic force is provided by the relatively short assembled elastics in each torsional elastic unit. As a result, even in such a configuration, the elastic body can be prevented from escaping radially outward in the central region in the vertical direction. In order to still be able to provide a stable configuration, it is possible for the outer ring part 52g to be for example reinforced, ie made of a relatively thick material or the like.

FIG. 19 is a view showing a form of the intermediate ring 42h. The intermediate ring essentially corresponds in structure to the intermediate ring 42g shown in FIG. 17, but any of the other configurations described in the previous embodiments may be employed. The mass portion 130h is fixedly disposed on the outer ring portion 52h. As a result, this mass part can shift the resonance frequency of the vibration system assembled with such an intermediate ring 42h to a suitable value, thereby additionally contributing to vibration damping. Furthermore, the vibration enhancement of the intermediate ring 42h having such a mass part 130h (vibration activation, Schwingu
ngsanregung) requires vibrational energy.
Then, the vibration energy is absorbed in the vibration system. As a result, vibrations that occur during the force transmission process can be suppressed.

FIGS. 20 and 21 are schematic diagrams of one torsional vibration damping device according to the present invention. The torsional vibration damper essentially corresponds in structure to the torsional vibration damper described earlier with reference to FIGS. 13 to 16. Therefore, see the preceding description for basic functional principles. At that time, in FIG. 20, the elastic window 26i of the hub disk (not shown) can be simply recognized. The torsional vibration damper shown in FIGS. 20 and 21 includes four intermediate rings 42i, 42i ', 42i ", and 42.
i "". As a result, each torsional elastic body unit can include five elastic bodies. Intermediate rings 42i, 42i ', 42
i "and 42i""are likewise elastic contact arms 5 for each torsion elastic unit.
4i, 54i ', 54i ", and 54i"". In such a configuration, the damping behavior of the torsional vibration damper may be even more similar to the damping behavior of a torsional vibration damper assembled with a very long elastic body (i.e., the obtain). However, there is no risk that the torsional elastics escape radially outwards due to their prestress and the centrifugal forces generated during operation. Due to the relatively large extent in the circumferential direction, in such a configuration, it is advantageous for the torsional vibration damping device to include only two torsional elastic units, each having five torsional elastic bodies.

As can be seen particularly in FIG. 21, the elastic contact arms 54i, 54 of the intermediate rings 42i, 42i '.
i 'is bent in the same direction in the axial direction in its radial end region and has intermediate rings 42i''and42i''.
i '''' elastic contact arms 54i '' and 54
i "" is bent axially in the opposite direction.
This allows, on the one hand, the intermediate rings 42i, 42i '.
Or on the other hand intermediate rings 42i '' and 42i ''
i '''are arranged in each case in the radial direction and are integrated with one another. The outer ring part 52i or 52i of the intermediate ring 42i or 42i "
i ″ is located radially outside the outer ring portion 52i ′ or 52i ″ ″ of the intermediate ring 42i ′ or 42i ″ ″. Correspondingly, intermediate ring 42i 'or 4
2i "" inner ring portion 50i "or 50
i "" is located radially outward of the corresponding inner ring portion 50i or 50i "of the intermediate ring 42i or 42i". Thus, even in such a relative arrangement, mutual interference of the respective inner and outer ring portions of the different intermediate rings can be avoided. However, at the same time, all the elastic contact arms 54i, 54i ', 54
i "and 54i""lie in a common plane with the attached hub disk.

FIG. 22 is a diagram showing another form of the torsional vibration damping device according to the present invention. In the case of this torsional vibration damper, an axial structure for receiving the intermediate ring 42k between the hub disk 12k and the cover plate 16k (or between the hub disk 12k and the entraining disk) in the axial direction. Space is provided. The cover plate 16k is provided with an elastic positioning flange 132k that is bent in the axial direction toward the hub disk 12k in the region of the restriction portion in the radial direction of the elastic window 30k. The elastic body positioning flange,
In function, it corresponds to the elastic positioning flange 132 known per se in FIG. This elastic positioning flange 132k, which is provided on the cover plate 16k on the one hand and on the entraining disk (not shown here) on the other hand, prevents the elastic body 32k from escaping in the axial direction and thereby its proper Is positioned so that it is held in the correct position. In the case of the embodiment shown in FIG. 22, sufficient structural space for the arrangement of the mass part 130h is provided between the cover plate 16k and the hub disk 12k, so that it is shown in FIG. Mass body part 1
It is possible to utilize an intermediate ring having 30h.

In the case of the torsional vibration damper according to the invention described above, the respective elastic bodies of the various torsion elastic units are formed relatively short; The elastic bodies cooperate in each case to provide elastic properties that correspond to the elastic properties of one long elastic body. However, based on the provision of the short elastic body, the problem of radial expansion of the elastic body at the longitudinal center portion of the elastic body is sufficiently eliminated. As a result, in the case of the torsional vibration damper according to the invention, it is possible to dispense with an elastic guide part provided with lubricating oil; therefore, in the case of the torsional vibration damper according to the invention. In particular, all requirements or problems arising with respect to the sealing of the elastic guides provided with such lubricating oil are eliminated.

In the case of elastic bodies which are short and thus formed with a comparatively small weight, outward bulging can be avoided even at relatively high rotational speeds, so that the elasticity of the respective torsion elastic units is reduced. The structural space provided for the body can be substantially limited to the elastic volume itself; no additional structural space used for receiving the expanding elastic body need be provided. If the elastic body contacts the hub disk or the entrainment disk or the cover plate in its radially outer region at very high rotational speeds, this also does not actually lead to wear. This is because, due to the relatively small weight of the elastic body, the contact pressure of the elastic body during such contact is relatively small.

It is obvious to a person skilled in the art that the features described for the various embodiments of the various assemblies, such as the arrangement of the inner ring part of the disc spring or the intermediate ring, can be combined with one another. is there. Therefore, for example, in the case of the form shown in FIG.
An elastic projection is provided on the elastic body 76e which engages a corresponding projection on the hub disk 12e and is thereby used for a rotationally fixed (relatively non-rotatable) connection between the hub disk 12e and the elastic body 76e. It may be.

[Brief description of the drawings]

1 is a sectional view of the torsional vibration damping device according to the present invention, taken along line II in FIG. 3;

FIG. 2 is a side view of a cover plate used in the case of the torsional vibration damping device according to the present invention in the direction of arrow II in FIG.

FIG. 3 is a schematic simplified plan view of a torsional vibration damper according to the present invention, used for explaining the principle of the present invention.

FIG. 4a is a view of the intermediate ring element of the torsional vibration damper according to the invention, and b is the line IVb-I at a.
It is sectional drawing by Vb.

FIG. 5 is a view of a hub disk used in the torsional vibration damping device according to the present invention.

FIG. 6 is a principle diagram for explaining the function of the torsional vibration damping device according to the present invention.

FIG. 7 is a view corresponding to FIG. 1 of another embodiment of the torsional vibration damping device according to the present invention.

FIG. 8 is a view of still another form of the torsional vibration damping device according to the present invention.

FIG. 9 is a view of still another embodiment of the torsional vibration damping device according to the present invention.

FIG. 10 is a view of still another form of the torsional vibration damping device according to the present invention.

FIG. 11 is a view of still another form of the torsional vibration damping device according to the present invention.

FIG. 12 shows a torsional vibration damper according to the prior art;
FIG.

FIG. 13 is a schematic plan view of yet another form of the torsional vibration damper according to the present invention in connection with a two-wheel flywheel.

FIG. 14 is a sectional view taken along line XIV-XIV in FIG. 13;

FIG. 15 is a cross-sectional view of the intermediate ring element in the case of the torsional vibration damping device of FIGS. 13 and 14;

FIG. 16 in use in the case of a clutch disc
FIG. 15 is an illustration of the torsional vibration damper shown in FIGS. 3 and 14.

FIG. 17 is a plan view of another intermediate ring element.

FIG. 18 is a sectional view corresponding to FIG. 15 of another intermediate ring element.

FIG. 19 shows the case where a vibrating mass part (Schwingungsmasseteil) is additionally arranged on the intermediate ring element,
FIG. 19 is a diagram corresponding to FIG. 18.

FIG. 20 shows a diagrammatic plan view of the elastic window of the hub disc, when four intermediate ring elements are provided, each with elastic contact arms, for one torsion elastic unit with five elastic bodies. FIG.

FIG. 21 is a sectional view taken along line XXI-XXI in FIG. 20, showing the intermediate ring element.

FIG. 22 is a view of still another form of the torsional vibration damping device according to the present invention.

FIG. 23 is a mechanical equivalent circuit diagram of a torsional vibration damping device including three torsion elastic body units each having three elastic bodies.

[Explanation of symbols]

8
Clutch disk 10, 10a, 10b, 10c, 10d, 10e, 10
f Hub 12, 12a, 12b, 12c, 12d, 12e, 12
f Hub disk 14, 14a, 14b, 14c, 14d, 14e
Entrainment disk 16, 16a, 16b, 16c, 16d, 16e, 16
f Cover plate 18, 18f
Pins 20, 20a, 20b, 20c, 20d, 20e
Support ring elements 26, 26a, 26f
Elastic window 28, 28a, 28f
Elastic window 30, 30a, 30f
Elastic window 32, 32a, 32b, 32c, 32d, 32e, 32
f elastic body 33
Torsion elastic unit 34, 36, 38
Control edge 40, 40f
Elastic body 42, 42a, 42b, 42c, 42d, 42e
Intermediate ring elements 42f, 42f ', 42g, 42h
Intermediate ring elements 42i, 42i ', 42i ", 42i""
Intermediate ring element 50, 50f, 50f '
Inner ring portions 50i, 50i ', 50i ", 50i""
Inner ring portions 52, 52f, 52f ', 52g
Outer ring portions 52i, 52i ', 52i ", 52i""
Outer ring portion 54, 54f, 54f ', 54g
Elastic contact arm 54i, 54i ', 54i ", 54i""
Elastic body contact arm 58
Control edge 60
Stopper surface 64
Projection 66, 68
Stopper surface 74, 74f
Friction device 76, 76a, 76b, 76c, 76e, 76f
Disc springs 80a, 82a
Axial passage opening 86b
Projecting part 88b
Recess 90d
Wave spring 102f
Main thin plate 114f
Elastic body 116f
Connecting part A
Axis

Claims (44)

[Claims] 1. A torsional vibration damper for damping torsional vibrations in a power transmission system of an internal combustion engine, in particular for a clutch disk, comprising a disk-shaped first damper member (14, 16; 14).
a, 16a; 14b, 16b; 14c, 16c;
d, 16d; 14e, 16e; 102f, 16f), and the first shock absorber member (14, 16; 14a, 16).
a; 14b, 16b; 14c, 16c; 14d, 16
d; 14e, 16e; 102f, 16f) rotatable about axis (A).
2; 12a; 12b; 12c; 12d; 12e;
f), comprising a torsion elastic device comprising at least one torsion elastic unit (33), wherein the at least one torsion elastic unit (33) is essentially successive in the circumferential direction Subsequently, at least two elastic bodies (3
2, 40; 32a; 32b; 32c; 32d; 32e;
32f, 40f, 114f), wherein the end located on the opposite side of the torsion elastic unit (33) in the circumferential direction is the first shock absorber member (14, 16; 1).
4a, 16a; 14b, 16b; 14c, 16c;
d, 16d; 14e, 16e; 102f, 16f) and the second shock absorber member (12; 12a; 12b; 12).
c; 12d; 12e; 12f) having a torsional elastic device cooperatively actuated for torsional vibration damping with respect to the axis (A) for said at least one torsional elastic unit (33). At least one elastic contact arm (54; 54f, 5
4f ';54g; 54i, 54i', 54i ", 54
i "") and said first shock absorber member (14,
16; 14a, 16a; 14b, 16b; 14c, 16
c; 14d, 16d; 14e, 16e; 102f, 16
f) and said second shock absorber member (12; 12a; 12)
b; 12c; 12d; 12e; 12f) at least one intermediate ring element (42; 42a; 42b; 42c; 4) rotatable about axis (A).
2d, 42e; 42f, 42f ';42g;42h;
2i, 42i '; 42i ";42i"');
The at least one elastic contact arm (54;
54f, 54f ';54g; 54i, 54i', 54
i ", 54i"") are at least two elastic members (32, 40; 32a; 32b; 32c; 3) of the at least one torsion elastic unit (33) in the circumferential direction.
2d; 32e; 32f, 40f, 114f) are arranged between the mutually facing ends, said at least one intermediate ring element (42; 42a;
42b; 42c; 42d, 42e; 54f, 54f ';
54g; 54i, 54i ', 54i ", 54
i ''') further comprises radial movement preventing means (64),
The at least two elastic bodies (32, 40; 32a; 3)
2b; 32c; 32d; 32e; 32f, 40f, 11
4f) the at least one elastic contact arm (5
54; 54f, 54f ';54g; 54i, 54i', 5
4i ", 54i""). A torsional vibration damper having an intermediate ring element that includes to prevent radially outward movement in the end region directed at 54i"). 2. A disk-shaped first shock absorber member (102f, 16) for damping torsional vibration in a power transmission system of an internal combustion engine, particularly for a clutch disk.
f), wherein the second shock absorber member (12; 12a; 12b; 12c; 12d; 12e; 1) rotatable about the axis (A) with respect to the first shock absorber member (102f, 16f).
2f), comprising a torsion elastic device comprising at least one torsion elastic unit (33), wherein said at least one torsion elastic unit (33) is essentially successive in the circumferential direction Subsequently, at least three elastic bodies (3
2f, 40f, 114f), in which case the end located on the opposite side of the torsion elastic body unit (33) in the circumferential direction is the first shock absorber member (102f, 16f).
f) and said second shock absorber member (12; 12a; 12)
b; 12c; 12d; 12e; 12f) having a torsional elastic device cooperating in response to actuation for torsional vibration damping, wherein the at least one torsional elastic unit (33) has an axis (A). ) At least one elastic contact arm (54f, 54) extending essentially radially
f ';54g; 54i, 54i', 54i '', 54
i '''') and the first shock absorber member (102f, 16f) and the second shock absorber member (1
2; 12a; 12b; 12c; 12d; 12e;
f) and at least two intermediate ring elements (42) rotatable about the axis (A) with respect to each other.
f, 42f ';42g;42h; 42i, 42i'; 4
2i ";42i"") with the elastic contact arms (54f, 54f"; 54) of the intermediate ring element.
g; 54i, 54i ', 54i ", 54i""), each of which has at least one torsion elastic unit (33) in the circumferential direction and which follows one after the other in the circumferential direction (32f, 40f, 114f). A torsional vibration damper having an intermediate ring element disposed between opposed ends of the torsional vibration damper. 3. Each intermediate ring element (42).
f, 42f ';42g;42h; 42i, 42i'; 4
2i ";42i"") is an elastic body (32f, 40f).
f, 114f) are the respective elastic contact arms (54
f, 54f ';54g; 54i, 54i', 54
i '', 54i ''''), characterized in that it further comprises radial movement preventing means in order to prevent radially outward movement in the end regions located opposite to each other. Torsional vibration damper. 4. Each intermediate ring element (4)
2: 42a; 42b; 42c; 42d, 42e; 42
f, 42f ';42g;42h; 42i, 42i'; 4
2i ";42i") are provided with an inner ring part (50; 50f, 50f "; 50i, arranged radially inward of said at least one torsion elastic unit (33).
50i ', 50i ", 50i"") and / or said at least one torsion elastic unit (3
The outer ring portion (5) disposed radially outside of (3).
52; 52f, 52f '; 52i, 52i', 52
i '', 52i '''') and said at least one elastic contact arm (54; 54f, 54
f ';54g; 54i, 54i', 54i '', 54
4. A torsional vibration damper according to claim 1, 2 or 3, characterized in that i "") extends substantially radially away from said inner or outer ring part. 5. At least one elastic contact arm (54) belonging to each intermediate ring element has at its circumferentially opposite end an elastic body (32,
40; 32a; 32b; 32c; 32d; 32e) provided with control edges (58) for contact;
And a protrusion (64) extending radially away from at least one elastic contact arm (54) in a radially outer end region of the control edge (58), wherein the radial movement preventing means (64) is provided. The torsional vibration damping device according to claim 1, wherein the torsional vibration damping device is formed by: 6. The first shock absorber member (14, 16;
14a, 16a; 14b, 16b; 14c, 16c; 1
4d, 16d; 14e, 16e; 102f, 16f) for elastic windows (28, 30; 28f, 30) for said at least one torsion elastic unit (33).
f), said second shock absorber member (12; 12a; 12b; 12c; 12d; 12e; 1)
2f), the corresponding elastic window (26; 26f)
The at least one torsion elastic unit (33)
For the first shock absorber member (1).
4, 16; 14a, 16a; 14b, 16b; 14c,
16c; 14d, 16d; 14e, 16e; 102f,
16f) and in said second shock absorber member (12;
12a; 12b; 12c; 12d; 12e; 12f) in the elastic window (26, 28, 30, 26).
The control edges (34, 36, 38) are respectively located at the circumferentially opposite ends of the torsional elastic body unit (33) at the circumferentially opposite ends of the torsional elastic units (33). The at least one elastic contact arm (54) of each intermediate ring element is formed for end contact and the elastic body (32,
40; 32a; 32b; 32c; 32d; 32e;
f, 40f, 114f) by means of radial parts provided for the contact in the axial direction at least partially in the second buffer element (12; 12a; 12b; 12c; 12).
d; 12e; 12f) the elastic window (26;
26f) with the control edge (34) formed at
The torsional vibration damper according to any one of claims 1 to 5, wherein the torsion vibration damper is located in a common plane perpendicular to the axis (A). 7. Each elastic contact arm (54f,
54f ';54g; 54i, 54i', 54i '', 5
4i '''') is the inner ring portion (50f, 50f).
f '; 50i, 50i', 50i ", 50i"")
And / or said outer ring portions (52f, 52
f '; 52i, 52i', 52i ", 52i"")
Is bent as follows in the area joined with
That is, the inner ring portion and / or the outer ring portion (50f, 50f '; 50i, 50i', 5
0i ", 50i", 52f, 52f "; 52i,
52i ', 52i ", 52i"") are axially offset with respect to said first shock absorber member (102f, 16f) and are bent so as not to overlap axially therewith. The torsional vibration damping device according to claim 6, wherein: 8. The inner ring portion and / or the outer ring portion (50f, 50f '; 50i, 50).
i ', 50i ", 50i", 52f, 52f ";
52. The torsional vibration damper according to claim 7, wherein the second damper member (12i) can be brought into contact with an axial side surface of the second damper member (12f). . 9. Each of the elastic contact arms (54f,
54f ';54g; 54i, 54i', 54i '', 5
4i ''') is formed near the radially inner or outer end region of the elastic window (26f) in the second shock absorber member (12f), respectively. The torsional vibration damping device according to claim 7 or 8, characterized in that: 10. Each intermediate ring element (4)
2f, 42f ';42g;42h; 42i, 42i';
42i ''; 42i ''''), wherein the radial extent of the elastic window (26f) is smaller than the radial extent of the elastic window (26f). Torsional vibration damper. 11. A first intermediate ring element (42).
f), the bent area of the elastic contact arm (54f) is bent in the axially opposite direction with respect to the bent area of the elastic contact arm (54f ') of another intermediate ring element (42f'). The torsional vibration damper according to any one of claims 7 to 10, wherein 12. A first intermediate ring element (42).
i, 42i '') of the elastic contact arm (54i; 54)
i '') is bent by the elastic contact arm (54) of another intermediate ring element (42i ', 42i'').
The torsional vibration damper according to any one of claims 7 to 11, characterized in that it is bent in the same direction in the axial direction with respect to the bent area of i ', 54i'''). 13. The intermediate ring element (42)
i ', 42i'") are radially extended by a respective intermediate ring element (42i, 42i).
i '') is smaller than the radial extent of the outer ring portion (52i ', 52i'') of the intermediate ring element (42i', 42i '''') which has a smaller radial extent. ) Are arranged radially inside the outer ring portion (52i, 52i '') of the respective intermediate ring element (42i, 42i '') and / or have a smaller radial extent. The intermediate ring element (42
i ', 42i "') inner ring portions (50i ', 5i'
0i ″ ′) are respectively different intermediate ring elements (4
2i, 42i ") inner ring portions (50i, 50i).
13. The torsional vibration damping device according to claim 12, wherein the torsional vibration damping device is arranged radially outward of i ''). 14. Each intermediate ring element (4)
2g) has only an outer ring portion (52g);
14. The method according to claim 1, wherein the at least one elastic contact arm is formed as a wedge-shaped contact point that is essentially pointed radially inward. Torsional vibration damper. 15. The torsional vibration damping device according to claim 14, wherein the outer ring portion (52g) is reinforced. 16. Each intermediate ring element (4)
2; 42a; 42b; 42c; 42d; 42e) have at least an inner ring portion (50), and said inner ring portion (50) is provided with said second shock absorber member (12; 12a; The torsional vibration damping device according to claim 6, characterized in that it is arranged axially adjacent to the radially inner region of (d); 17. The at least one intermediate ring element (42; 42a; 42b; 42c; 42d)
In the area of the at least one elastic contact arm (54), the second damper member (12; 12) is axially radially outward from the inner ring portion (50).
The torsional vibration damper according to claim 16, characterized in that it is bent towards a; 12b; 12c; 12d). 18. The second shock absorber member (12; 12).
The torsional vibration damping device according to any of the preceding claims, characterized in that a; 12b; 12c) are configured essentially flat. 19. The second shock absorber member (12d; 1)
2e) comprises the at least one elastic contact arm (5)
4) in the radial region corresponding to 4), radially outwardly in the axial direction with said intermediate ring element (42d; 42).
2. The method as claimed in claim 1, wherein the first member is bent toward e).
The torsional vibration damping device according to any one of claims 17 to 17. 20. The at least one intermediate ring element (42e) is configured to be essentially flat, and the second shock absorber member (12e) is connected to the at least one elastic contact arm (54). 17. The torsional vibration damper according to claim 16, characterized in that it is bent axially outward in the radial region corresponding to the at least one intermediate ring element (42e). apparatus. 21. The first shock absorber member (14, 1).
6; 14a, 16a; 14b, 16b; 14c, 16
c; 14d, 16d; 14e, 16e; 102f, 16
f), the second shock absorber member (12; 12)
a; 12b; 12c; 12d; 12e; 12f) adjacent to the first disk element (14;
14a; 14b; 14c; 14d; 14e; 102f).
And the second shock absorber member (12; 12)
a; 12b; 12c; 12d; 12e; 12f) in the axial direction with respect to the first disc element (14; 14).
a; 14b; 14c; 14d; 14e; 102f) and on the opposite side and preferably in the radially outer region, said first disk element (14; 1).
4a; 14b; 14c; 14d; 14e; 102f) which are fixedly connected to the second disk element (16;
16a; 16b; 16c; 16d; 16e; 16f) and the respective intermediate ring elements (42; 42a; 42b; 42c; 42d; 42e; 4).
2f, 42f ') and / or the outer ring portion (50; 52f, 52).
f ') in the axial direction of said second shock absorber member (12; 12).
12b; 12c; 12d; 12e; 12f) and the first disk element (1
5. The torsional vibration damper according to claim 4, wherein the torsional vibration damper is arranged between the second disk element and the second disk element. 22. The first disk element (1)
4; 14a; 14b; 14c; 14d; 14e) are radially inward in the region of the support ring element (20; 20).
20b; 20c; 20d; 20e) and the inner ring portion (52) of each intermediate ring element (42; 42a; 42b; 42e) is non-rotatable. Element (1
22. The torsional vibration damper according to claim 21, characterized in that it is arranged between the second damper member (12; 12a; 12b; 12e). 23. The support ring element (20)
Are axially aligned with the first disk element (14; 1).
4a; 14b) and the second shock absorber member (12; 12).
a; 12b) extending between the inner ring part (5) of the respective intermediate ring element (42; 42a; 42b) on its outer peripheral surface.
23. The torsional vibration damper according to claim 22, wherein an emergency guide for 0) is formed. 24. A friction device (74; 74f) is provided, said friction device being adapted to provide said second damping member (12; 12a; 12) to provide a torsional vibration damping friction force.
b; 12c; 12d; 12e; 12f) and the first buffer member (14, 16; 14a, 16a; 14b, 1).
6b; 14c, 16c; 14d, 16d; 14e, 16
e; 102f, 16f). 25. The support ring element (20; 2).
0a; 20b; 20c; 20d), if necessary, with the intervention of friction lining means in the axial direction of said second damping element (12; 12a; 12b; 12c; 12).
d) and the second shock absorber member (12; 12a; 12b; 12c; 12d) and the second disk element (16; 16a; 16b; 16).
c; 16d) and the elastic device (76; 7)
6a; 76b; 76c; 90d) are connected to the support ring element (20; 20a; 20b; 20c; 20d).
The second shock absorber member (12; 12a; 12b; 12)
The torsional vibration damping device according to claim 24, wherein a prestress is applied in a direction toward c; 12d). 26. The second disk element (16)
e) is axially in contact with said second shock absorber member (12e) with the intervention of friction lining means, if necessary, and said second shock absorber member (12e).
e) an elastic device (76e) provided between the support ring element (20e) and the second disk element prestresses in a direction toward the second shock absorber member (12e). 3. The method according to claim 2, wherein
5. The torsional vibration damping device according to 4. 27. The disk drive according to claim 27, wherein the elastic device comprises a disc spring (76; 7).
6a; 76b; 76c; 76e; 76f), an elastic element (76; 76a; 76b; 76c) formed by a ring spring, a wave spring (90d), and the like.
90d; 76e; 76f);
The torsional vibration damping device according to claim 25 or claim 26. 28. The resilient element (76b) abuts a second shock absorber member (12b) in a region radially inward and by at least one axially directed protrusion (86b). The second shock absorber member (1
Complementary recesses (8) in the radially inner region of 2b)
28. The torsional vibration damper according to claim 27, characterized in that it engages with 8b). 29. The first shock absorber member (1)
4, 16; 14a, 16a; 14b, 16b; 14c,
16c; 14d, 16d; 14e, 16e; 102f,
16f) and said second shock absorber member (12; 12a; 1)
2b; 12c; 12d; 12e; 12f) for limiting the rotational displacement.
0, 66, 68; 18f, 116f). 30. The rotation displacement limiting means (18, 60,
66, 68) correspond to the first buffer member (14, 1).
6; 14a, 16a; 14b, 16b; 14c, 16
c; 14d, 16d; 14e, 16e; 102f, 16
f) and said second shock absorber member (12; 12a; 1)
2b; 12c; 12d; 12e; 12f) and circumferentially acting stopper means (18, 60, 66, 6)
8; 107, 116). The torsional vibration damping device according to claim 29, characterized in that it comprises: 31. The first shock absorber member (102f,
31. The torsional vibration damper according to claim 30, wherein the stopper means (18f) associated with 16f) acts directly on the stopper means (116f) associated with the second shock absorber member (12f). . 32. Each intermediate ring element
A first stopper means (68) is provided which cooperates with a stopper means (18) associated with said first shock absorber member (14, 16), and said second shock absorber member (12). 31. Second stop means (66) cooperating with a stop means (60) associated with the first and / or second intermediate ring element is provided. Torsional vibration damper. 33. Each intermediate ring element (4)
2) The first and second stopper means (6
6, 68) are formed by essentially radially extending stop surfaces (66, 68), the stop surfaces extending circumferentially away from the respective elastic contact arms (54). 33. The torsional vibration damper according to claim 32, characterized in that it is formed in a part (64). 34. The torsional vibration damping device having the configuration according to claim 21 and claim 30, wherein said stopper means (18; 18f) belonging to said first damping member (14, 16; 102f, 16f). Are formed by at least one pin element (18; 18f) connecting the first disk element (14; 102f) to the second disk element (16; 16f). Shock absorber. 35. The stopper means (60) associated with the second shock absorber member (12) extends essentially radially in a region radially outside the second shock absorber member. 35. A torsional vibration damper according to claim 30, wherein the torsional vibration damper is formed by a stop surface (60). 36. An elastic body (32, 40; 32f, 40f, 1) of at least one torsion elastic body unit (33).
14. The torsional vibration damper according to claim 1, wherein 14 f) has the same spring constant. 37. The elastic bodies (32, 40; 32f, 4f) of the at least one torsion elastic body unit (33).
36. The torsional vibration damper according to claim 1, wherein 0f, 114f) have different spring constants. 38. The torsional vibration damper having the configuration according to claim 6 or claim 21, wherein the elastic window (26) in the second shock absorber member (12a) is provided.
a) is directed radially inward to the first shock absorber member (1).
4a, 16a) having a greater extent than the corresponding elastic windows (28a, 30a) in the first and second disc members (14a, 16a);
And the first and second disk members (14a, 16
In the area corresponding to the radially inwardly extending portion of the elastic window (26a) of the second shock absorber member (12a) in (a), the axial passage opening ( 80a, 82a) are provided. 39. The first shock absorber member (14, 1).
6; 14a, 16a; 14b, 16b; 14c, 16
c; 14d, 16d; 14e, 16e; 102f, 16
f) or said second shock absorber member (12; 12a;
12b; 12c; 12d; 12e; 12f) are the inputs of the clutch discs (8), in particular the entrainment discs (14;
14a; 14b; 14c; 14d; 14e; 102f).
And each of said separate members is an output of a clutch disk (8), in particular a hub disk (12; 12).
12b; 12d; 12e; 12f). The torsional vibration damping device according to any one of the preceding claims, characterized in that: a; 40. The output portion (12; 12a; 12b; 12c; 12) of the first and second shock absorber members.
d; 12e; 12f) are the hubs (10;
10a, 10b; 10c; 10d; 10e; 10f).
40. The torsional vibration damper according to claim 39, wherein the torsional vibration damper is fixedly connected, preferably by welding or the like. 41. The support ring element (20; 2).
0a; 20b; 20c; 20d; 20e) is the hub (1
23. The torsional vibration damper according to claim 22, wherein the torsional vibration damper is rotatably mounted around the axis (A) at 0; 10a, 10b; 10c; 10d; 10e). 42. A torsional vibration damper for damping torsional vibrations in a power transmission system of an internal combustion engine, in particular for a clutch disk, comprising a disk-shaped first damper member (14, 16; 14).
a, 16a; 14b, 16b; 14c, 16c;
d, 16d; 14e, 16e; 102f, 16f), and the first shock absorber member (14, 16; 14a, 16).
a; 14b, 16b; 14c, 16c; 14d, 16
d; 14e, 16e; 102f, 16f) rotatable about axis (A).
2; 12a; 12b; 12c; 12d; 12e;
f) wherein the at least one torsion elastic unit (33) comprises at least one torsion elastic unit (33), wherein the at least one torsion elastic unit (33) essentially follows one another in the circumferential direction. 32 at least two elastic bodies (32, 40; 32a; 32b; 32c; 32d; 32)
e; 32f, 40f, 114f), and the ends of the torsion elastic body unit (33) located on the side opposite to the circumferential direction are the first shock absorber members (14, 16; 14a, 1f).
6a; 14b, 16b; 14c, 16c; 14d, 16
d; 14e, 16e; 102f, 16f) and said second shock absorber member (12; 12a; 12b; 12c; 12).
d; 12e; 12f) having a torsional elastic device cooperatively actuated for torsional vibration damping, essentially for the at least one torsional elastic unit (33) with respect to axis (A). And at least one elastic contact arm (54i) extending radially to said first shock absorber member (14, 16; 14a, 16).
a; 14b, 16b; 14c, 16c; 14d, 16
d; 14e, 16e; 102f, 16f) and said second shock absorber member (12; 12a; 12b; 12c; 12).
d; 12e; 12f) at least one intermediate ring element (4) rotatable about axis (A).
2: 42a; 42b; 42c; 42d, 42e; 42
f, 42f ';42g;42h; 42i, 42i'; 4
2i ";42i""), wherein the at least one elastic contact arm (54; 54f, 54
f ';54g; 54i, 54i', 54i '', 54
i ′ ″) is the circumferential direction of the at least two elastic bodies (3) of the at least one torsion elastic body unit (33).
2, 40; 32a; 32b; 32c; 32d; 32e;
32f, 40f, 114f) between the opposite ends of said disk-shaped first shock absorber member (14, 16; 14a, 16a; 14b, 16b).
b; 14c, 16c; 14d, 16d; 14e, 16
e; 102f, 16f) are the first disk elements (14; 14a; 14b; 14c; 14d; 14e; 1).
02f) and the first disk element (14; 1
4a; 14b; 14c; 14d; 14e; 102f) are axially spaced from and fixedly connected to the second disk element (1
6; 16a; 16b; 16c; 16d; 16e;
f), said second shock absorber member (12; 12)
a; 12b; 12c; 12d; 12e; 12f) are configured essentially in the form of a disc and are axially oriented with said first and second disc elements (14; 14a; 14).
e, 16; 16a, 16e; 102f, 16f) and the at least one intermediate ring element (42; 42a; 42b; 42c; 42).
d; 42e; 42f, 42f ';42g;42h; 42
i, 42i '; 42i ";42i") are at least their elastic contact arms (54; 54f, 54f'; 5) for each torsion elastic unit (33).
4g; 54i, 54i ', 54i ", 54i"")
In the area of the second shock absorber member (12; 12a; 1)
2b; 12c; 12d; 12e; 12f) together with an intermediate ring element, which lies in a common plane essentially perpendicular to the axis (A). 43. Each intermediate ring element (4)
2: 42a; 42b; 42c; 42d; 42e; 42
f, 42f ';42g;42h; 42i, 42i'; 4
42. The torsional vibration damper according to claim 1, wherein 2i ";42i"") is formed by a single disk member. 44. Intermediate ring elements (42; 42a; 42b; 42c; 42d; 4) rotatable with respect to each other.
2e; 42f, 42f ';42g;42h; 42i, 4
2i '; 42i ";42i"') is the number of the elastic members (32,
40; 32f, 40f, 114f) and one less than the number of each intermediate ring element (42;
42a; 42b; 42c; 42d; 42e; 42f, 4
2f ';42g;42h; 42i, 42i'; 42
i ''; 42i '''') are elastic contact arms (54; 54) for each torsion elastic unit (33).
f, 54f ';54g; 54i, 54i', 54
i '', 54i ''''). The torsional vibration damping device according to any one of the preceding claims, characterized in that: